Spring coiling machine



Nov. 21, 1961 E. E. FRANKS, JR

SPRING COILING MACHINE 8 Sheets-Sheet 1 Filed Aug. 4, 1958 FIG. I

..| islnk INVENTOR. EDWARD E. FRANKS JR.

1 m b 07 M ATTORNEYS Nov. 21, 1961 E. E. FRANKS, JR 3,009,505

SPRING COILING MACHINE Filed Aug. 4, 1958 8 Sheets-Sheet 2 IN V EN TOR. EDWARD E. FRANKS IR.

ATTORNEYS Nov. 21, 1961 E. E. FRANKS, JR

SPRING COILING MACHINE Filed Aug. 4, 1958 8 Sheets-Sheet 3 FIG. 3

FIG. 9 l4 IN V EN TOR. EDWARD E. FRANKS 3R.

ATTORNEYS Nov. 21, 1961 E. E. FRANKS, JR 3,009,505

SPRING COILING MACHINE Filed Aug. 4 1958 8 Sheets-Sheet 4 IN V EN TOR. EDWARD E. FRANKS JR.

ATTORNEYS Nov. 21, 1961 E. E. FRANKS, JR 3, 5

SPRING COILING MACHINE Filed Aug. 4, 1958 8 Sheets-Sheet 5 232 FIG? 8 T 264 u I12 250 I08 I98 F|G.8 262 as 238\ i 0 & R :Ilsgl 246 244 4/ IN V EN TOR.

5 EDWARD E. FRANKS JR.

ML P/HL ATTORNEYS Nov. 21, 1961 E. E. FRANKS, JR 3,009,505

SPRING COILING MACHINE Filed Aug. 4, 1958 8 Sheets-Sheet 6 FIG. II

68 FIG. I5

I I40 COUNTER I IN VEN TOR. WARD E. FRANKS DR.

f/mlmwww ATTORNEYS Nov. 21, 1961 E. E. FRANKS, JR 3,009,505

SPRING COILING MACHINE Filed Aug. 4, 1958 8 Sheets-Sheet 7 FIG, FEED PORTION OF CYCLE GAMSHAFT STARTS HERE HALFWAY THROUGH FEED IN 4TH.CYCLE CAMSHAFT STOPS HERE HALFWAY THROUGH FEED IN I ST. CYCLE LEADING END (I SPRING FED AND SHAPED DURING FIRST HALF OF IST. CYCLE TRAILING END OF SPRING FED AND SHAPED DIRING SECOND HALF OF 4 TH.OYOLE IMPULSE TO CLUTCH SOLENOlD HERE CUT-OFF HERE LEADING PORTION OF SPRING MADE DURING FIRST HALF OF IsT.cYcLE, ARBOR ASORANKPW MOVES FROM 8 TO 0 IN THE SECOND HALF OF ITs SINGLE REVOLUTION. OAMSHAFT STOPS WHEN CRANKPIN REAcHEs c.

J S /I] PORTION OF SPRING MADE DURING SECOND HALF OF IsT.cYcLE. 'Q OAMSHAFT IDLE As CRANKPIN MovEs"I=R*oM c 10' D.

PORTION OF SPRING MADE DuRINe wHoLE OF 2 ND. cYcLE. cAMsHAFT IDLE I 3 PORTION OF SPRING MADE DURING wHDLE OF sRDcYcLE. CAMSHAFT IDLE PORTION OF SPRING MADE DURING FIRST HALF OF I 4TH.cYcLE.cAMsHAI=T IDLE As ORANKPIN MovEs (e) D FROM 5 TO C. CUTTER TRAILING PORTION OF SPRING MADE DuRINe 1 sEcoND HALF OF 4TH. cYcLE As ORANKPIN MovEs FROM 0 TO D, IN THE FIRST HALF OF :1 D ITS SINGLE REVOLUTION. CAMSHAFT STARTS WHEN CRANKPIN REAcHEs 0. SPRING Is ARDDRI S CUT-OFF wHEN CRANKPIN REACHES A.

CAMSHAFT CAMSHAFT IDLE CAMSHAFT I ROTATES T ROTATES INVENTOR.

r: EDWARD E. FRANKS JR.

I ITI-LcYcLE 3RD.CYOLE 2ND.cYcLE ISIZCYCLEl W I H Q '4 ATTORNEYS Nov. 21, 1961 E. E. FRANKS, JR 3,009,505

SPRING COILING MACHINE Filed Aug. 4, 1958 8 Sheets-Sheet 8 FIG. I9

FIG. 2|

s SOLENOID 0 c oo l [vi 370 R I SOLENOID ER, fiw

374 INVENTOR. W EDWARD E. FRANKS JR. BY Q J- I ML M ATTORNEYS United States Patent 3,009,505 SPRING COILING MACHINE Edward E. Franks, Jr., Litchfield, Conn., assignor to The Torrington Manufacturing Company, Torrington, Conn., a corporation of Connecticut Filed Aug. 4, 1958, Ser. No. 752,728 6 Claims. (Cl. 153-2) The invention relates to a spring coiling machine and more particularly to a machine of the type wherein the feed ro-lls are driven intermittently by mechanism which includes an oscillating gear segment.

Spring coiling machines of the oscillating segment type have many advantages, but they have been subject to the serious limitation that the maximum length of wire available for each spring was that length of wire fed by the segment when oscillating once through its maximum angle. Springs requiring longer wire lengths have had to be made on other machines of a different and otherwise less desirable type, and in a spring manufacturing plant such other machines may not be always conveniently available.

An important object of the invention is to provide a spring coiling machine of the segment type which is so constructed and arranged that the length of wire for each spring can be much greater than the length that can be fed during a single oscillation of the segment.

Another important object of the invention is to pro.- vide means that enables a spring coiling machine of the segment type to serve, under certain conditions, for coiling larger Wire than would otherwise be possible.

A more specific object of the invention is to provide a machine of the type specified, so constructed and arranged that the camshaft makes only one rotation within each successive period of time required for an integral plurality of sequential gear segment oscillations.

Another more specific object of the invention is to provide a machine wherein the camshaft makes one rotation at normal speed during each of a succession of series of cycles with an integral plurality of cycles in each series.

Still another object of the invention is to provide a machine as last above-described and having means for readily changing the number of machine cycles in each series.

Other and more specific objects of the invention are to provide various features of constructiion and arrangement which make possible the attainment of the beforestated general and specific objects.

The drawings show three embodiments of the invention and such embodiments will be described, but it will be understood that various changes may be made from the constructions disclosed, and that the drawings and description are not to be construed as defining or limiting the scope of the invention, the claims forming a part of this specification being relied upon for that purpose.

Of the drawings:

FIG. 1 is a front view of a machine embodying the invention.

FIG. 2 is a vertical sectional view taken along the line 2-2 of FIG. 1, but omitting the base of the machine.

FIG. 3 is a fragmentary sectional view, the right portion being taken along the line 3-3 of FIG. 1 and the left portion being taken along the line 3 3 of said FIG. 1.

FIG. 4 is a fragmentary sectional view taken along the line 4-4 of FIG. 1.

FIG. 5 is a fragmentary sectional view taken along the lines 5-5 of FIGS. 3 and 4.

FIG. 6 is a fragmentary front and sectional view, the sectional portion of the view being taken along the lines 6-6 of FIGS. 3 and 4.

FIG. 7 is a fragmentary front and sectional view, the sectional portion of the view being taken along the line 7-7 of FIG. 3.

FIG. 8 is a sectional view taken along the' line 8'-8 of FIG. 7.

FIG. 9 is a fragmentary sectional view similar to thelower left portion of FIG. 3, but showing alternative parts in position.

FIG. 10 is a fragmentary sectional view also similar to the lower left portion of FIG. 3, but showing other alternative parts in position.

FIG. 11 is a fragmentary sectional view also similar to the lower left portion of FIG. 3, but showing an alternative construction, this View being taken along the line 11-11 of FIG. 12.

FIG. 12 is a fragmentary rear view of. the machine provided with the alternative construction shown in FIG. 11.

FIG. 13 is an enlarged fragmentary sectional View taken along, the lines 13-13 of FIGS. 12 and 14.

FIG. 14 is a fragmentary view taken in the direction of the arrows 14-14 of FIG. 12.

FIG. 15 is a diagram of electrical connections.

FIG. 16 is a schematic view of the gear segment and related parts.

FIG. 17 is a diagram showing successive steps in making a spring.

FIG. 18 is a view summarizing the several steps shown in FIG. 17.

FIG. 19 is a side view of a spring receiving trough and associated mechanism'that may constitute a portion of a machine embodying the invention, some of the illustrated parts being alternative to some of the parts shown in FIGS. 11 to 15.

FIG. 20 is an enlarged front view of the trough and mechanism shown in FIG. 19.

FIG. 21 is a diagram of electrical connections for the mechanism shown in FIGS. 19 and 20.

General organization FIGS. 1 to 8 of the drawings show a machine generally similar to that shown in Patent 2,119,002 to Bergevin et al. but having different and additional mechanism to some of which the present invention more particularly relates.

The machine comprises front and rear upright frame members 12 and 14 mounted on a suitable base 16. The various wire feeding and coiling devices are mounted on the front frame member 12 and the several mechanisms for operating said devices are mounted between the members 12 and 14. The machine may have cover plates at the sides and top thereof secured to said frame members, but such plates are omitted from the drawings for clarity of illustration.

The line of wire feed is indicated at 18 in FIG; 1, the wire being fed through a preliminary guide 20' and between pairs of cooperating rotatable feed rolls 22, 24 and 26, 28. The feed rolls when rotated serve to project the wire toward the left so as to be engaged by wire coiling tools or devices as hereinafter described in detail. Wire guides 30 are provided between the feed rolls 22', 24 and the feed rolls 26, 28 and additional wire guides 32 are provided between the feed rolls 26, 28 and the coiling devices.

The feed rolls 22, 24 are carried by shafts 34, 36 and the feed rolls 26, 28 are carried by shafts 38, 40, all of the said shafts being mounted in bearings in the frame members 10 and 12. The shafts 38, 40 are connected by meshing gears 42, 44 and the shafts 34, 36 are connected by similar meshing gears which are not shown. The shafts 34 and 38 for the upper feed rolls 22. and 26. are capable of slight vertical movement at the front, being mounted in vertically movable bearing blocks 46 and 48. A bowed spring 50 is provided which rests at its ends upon the bearing blocks 46 and 48 and which is engaged by a handwheel 52 engaging a threaded member 54. By turning the handwheel 52, the spring 50 may be relatively flattened to apply downward pressure to the bearing blocks 46 and 48 and to thus apply downward pressure to the feed rolls 22 and 26 so that they grip the wire.

The lower feed roll shafts 36 and 40 are extended toward the rear and beyond the rear frame member 14, and said shafts are provided respectively with gears 56 and 58. The gear 58 is clearly shown in FIG. 2, but the gear 56 is shown only by a dotted line in FIG. 1. Both of said gears 56 and 58 mesh with a gear 60 on a longitudinal feed shaft 62 mounted in suitable hearings in the frame members 12 and 14. The feed shaft 62 is rotated by the mechanism and in the manner to be described and, when rotated, it rotates the shafts 36 and 40 which in turn rotate the several feed rolls for feeding the wire toward the left as previously stated.

A longitudinal main drive shaft 64 is provided, this being mounted in suitable hearings in the frame members 12 and 14. The drive shaft 64 is continually driven, as for instance by a motor, not shown, the motor being connected with the shaft by belts engaging a belt pulley 66 secured to said shaft. A bull or crank gear 68 is rotatable on a stub shaft 70 projecting forwardly from the rear frame member 14. The gear 68 meshes with a pinion 72 on the main drive shaft 64. All operative parts of the machine are driven by said gears 72 and 68.

The gear 72 may be directly connected to the drive shaft 64, but it is preferably connected indirectly by means of a clutch 90 controlled by a manually operable lever 92. By means of the clutch 90 the operation of the machine can be started and stopped without starting and stopping the motor and the drive shaft 64.

As shown in FIGS. 1 and 2, a mechanism may be provided for manually operating the machine or parts thereof for set-up or other purposes. A handwheel 94 located at the front of the machine is carried by a longitudinal shaft 96 rotatably and longitudinally movable in bearings in the front and rear frame members 12 and 14. A pinion 98 is provided on the shaft 96, and this pinion may mesh with a gear 100 connected with the driven element of the clutch 90. When the parts are in the positions shown in FIG. 2, the handwheel is idle. The handwheel 94 and the shaft 96 can be moved forwardly to cause the pinion 98 to mesh with the gear 100, forward movement being limited by a collar 101. When the pinion 98 meshes with the gear 100, the handwheel can be used to slowly move all of the parts, including the feed rolls. The handwheel 94 and the shaft 96 are normally held in their idle positions by a spring pressed detent 102.

A gear segment 74 is located adjacent the gear 68 and at the front thereof, said segment having a radial arm 76 which is carried by a rockshaft 78 mounted in bearings, not shown, in the front and rear frame plates 12 and 14. The gear segment 74 meshes with a feed gear 80 on said feed shaft 62, the gear 80 being connected with the shaft 62 by a unidirectional clutch 82. The radial arm 76 of the gear segment has a radial groove 84 and the bull or crank gear 68 carries a normally eccentric roller 86 which enters and fits said groove 84. The roller 86 is adjustable relatively to the gear 68 by means of a screw 88, and by rotation of the screw the extent of roller eccentricity can be changed. The roller 86 has the function of a crankpin and it is hereinafter so referred to. With the crankpin 86 in an eccentric position, the gear segment 74 is caused to make one oscillation during each gear rotation, and as the segment oscillates it rotates the gear 80 successively in opposite directions and the unidirectional clutch 82 operates the shaft 62 in only one direction and intermittently. The clutch 82 is so constructed and connected that the shaft 62 is operated only in the clockwise direction as indicated in FIG. 1, this direction corresponding to rotation of the feed rolls in their feeding directions as also indicated in FIG. 1. The extent of rotation of the shaft 62 and of the feed rolls during each rotation of the gear 68 can be changed by changing the eccentricity of the crankpin 86. Thus the length of Wire fed during each segment oscillation can be adjusted.

As the wire is gripped between the feed rolls and is fed forwardly, that is, toward the left as viewed in FIG. 1, it passes over or under an arbor 104 and it is forced against a coiling point 106 which deflects the wire downwardly or upwardly, according to the adjustment of the coiling tools, and around the arbor 104 to produce either a right or a left-hand spring. The arbor 104 is shown below the level of the line of wire feed and the wire is deflected downwardly around the arbor for a right-hand spring. The arbor 104 is carried by a tool holder 108, and a guide 107 on the tool holder holds the wire close to the top of the arbor.

A pitch tool 110 may be also mounted on the holder 108. The function of the pitch tool 110 is to longitudinally deflect each coil after it has been formed, and to provide the necessary pitch or space between adjacent coils or convolutions. Means are provided for adjusting the pitch tool longitudinally relatively to the holder 108, and the pitch tool may be so adjusted during the coiling operation. The mechanism fOr moving the pitch tool during coiling is hereinafter described in detail. The diameter of the coil formed by the coiling point 106 is determ ned by the spacing of said coiling point from the arbor 104. Means are preferably provided for adjusting the coiling point to vary said spacing and to thus vary the diameter, and the coiling point may be so adjusted during the coiling operation. The mechanism for moving the coiling point during coiling is hereinafter described in detail. The two mechanisms serving respectively to change the pitch and to change the diameter are hereinafter sometimes referred to collectively as mechanism for changing the shape of the coils of the spring.

Following the feeding of a predetermined length of wire and following the completion of a series of coils to constitute a spring, a cut-off mechanism comes into operation to eifect the severing of the wire at the arbor 104. The cut-off mechanism includes two oscillatory heads 112 and 114 above and below the arbor 104. When righthand springs are being coiled, a cutting tool 116 is mounted in the lower head 114 so as to cooperate with the arbor 104 for cutting the wire. When left-hand springs are being coiled, the arbor is positioned above the line of wire feed and the wire is deflected upwardly around the arbor. For a left-hand spring a cutting tool, not shown but similar to the tool 116, is mounted in the upper head 112 so as to cooperate with the arbor for cutting the wire.

For operating the cut-off mechanism and the diameter mechanism and the pitch mechanism, there is provided a longitudinal camshaft 118 rotatable in bearings in the front and rear frame members 12 and 14. The camshaft 118 is best shown in FIG. 3. A gear 120, best shown in FIG. 2, is connected with the gear 68 and it may be integral therewith. The gear 120 meshes with a gear 124 on the camshaft 118. The gears 120 and 124 preferably have the same number of teeth and they therefore rotate at the same speed. The gear 124 rotates the camshaft and said gear makes one rotation during each oscillation of the gear segment. In accordance with the invention the gear 124 is connected with the camshaft indirectly rather than directly, and the camshaft does not necessarily rotate at the same speed as the gear. The connection between the gear 124 and the shaft 118 will be hereinafter described in detail.

Cut-0H mechanism Referring particularly to FIGS. 1, 3, 4 and 5, the cutoff mechanism includes the two before-mentioned heads 112 and 114, each head being adapted to carry a cutting tool such as 116 adapted to cooperate with the arbor 104. As best shown in FIG. 4, the heads 112 and 114- are mounted on or formed integrally with horizontal shafts 126 and 128 rotatably mounted in bearings in the frame members 12 and 14. Secured to the upper shaft 126 is a transversely projecting arm 130 which is pivotally connected to a link 132. The link 132 extends downwardly and is connected at its lower end with an arm 134 mounted on a longitudinal pivot shaft 136. The arm 136 carries a roll 138 bearing on a cam 140 mounted on the camshaft 118. The cam 140 is so designed that an oscillatory movement is imparted to the arm 134 and the upper cutter shaft 126- during each complete rotation of the camshaft 118. Turning movement of the upper cutter shaft 126 is imparted to the lower shaft 128 by means of inter-meshing gear segments 142 and 144 mounted on the shafts, so that the cutter heads 112 and 114 are turned but in opposite directions. As the link 132 is moved downwardly, the upper head 112 is moved in its counterclockwise cutting direction and the lower head 114 is moved in its clockwise cutting direction. After movement of the shafts and heads in their cutting directions, they are moved in their reverse directions by a suitable spring, not shown. An adjustable screw 146 is engageable with the arm .131) to limit movements of the shafts and cutter heads in their said reverse directions. From the foregoing description it will be apparent that the cut-01f mechanism is actuated by the cam 140* on the camshaft 118. There will be one cut-off action during each camshaft rotation.

The movements in the cutting directions are preferably adjustable. As shown, the link 132 extends loosely through a hole in the arm 13%, and a sleeve 148 surrounds the link above said arm. The upper portion of the link 132 is threaded and a nut 150 on said threaded portion engages the top of the sleeve. When the nut 150 is adjusted upwardly, the effective length of the link 132 is increased and there is a corresponding decrease in the extent of the cutter head movements from the positions determined by the stop screw 146.

In order that each cutting tool, such as 1.16, may be properly positioned longitudinally for engaging the particular spring coil required to be cut, the heads 112, 114 and the shafts 126, 128 are preferably adjustable longitudinally. As shown, the shafts 126 and 128 carry adjustment blocks 152 and 154 which are nonrotatable. The blocks are held to prevent longitudinal movements relatively to their shafts, said looks being interposed between said gear segments 142, v144 and collars 156, 158 secured to the shafts. Longitudinal screws 1'60 and 162 extend into threaded holes in the respective blocks 152 and 154. The screws extend through the front frame member 12, and collars on the screws prevent longitudinal movement thereof. The front ends of the screws are exposed for engagement by a wrench or otherwise. When either screw is turned, the corresponding shaft and cutter head are moved forwardly or rearwardly to properly position the corresponding cutter.

Pitch control mechanism Referring particularly to FIGS. 1, 3, 4 and 6, the pitch control mechanism includes the before-mentioned pitch tool 110 and means for supporting and controlling said tool. The tool 111 is at the front end of a long slender stern 164 which fits with a tube 166. The tube 166 extends through and his one of two similar superposed holes in the tool holder 8, and it is shown as being in the lower hole. Secured to the front frame member 12 and projecting rearwardl-y therefrom are two superposed guide rods 168 and 170. A block 172 is provided which has holes for receiving and fitting said guide rods, the block being movable forwardly and rearwardly. A plate 174 is provided at the left of said block 172, as viewed in FIG. 6, and the block and plate have registering halfcylindrical grooves which receive and fit the tube 166.

6 By means of screws 176 and 178 the plate 174- can be pressed toward the block 172 to clamp the tube 166. Other grooves are provided at 180 to receive the tube 166 when it is in the upper hole in the tool holder.

A lever 182 is pivoted for movement about a transverse horizontal axis at 184. Connected with the lever is 2. depending arm 186 having a fork which embraces a button 188 on the block 170. Counter clockwise movement of the lever 182 serves to move the block 170 and the tool 116' forwardly, and reverse movement is effected by springs 1913 and 192 surrounding the guide rods 168 and 1711. A link 194 engages the rear portion of the lever 182 and extends downwardly therefrom. The link 1% is connected at its lower end, as shown in FIG. 6, with a transverse lever 16- pivotally mounted on said longitudinal shaft 1%. A transverse lever 200 is positioned above the lever 196 and is pivotally mounted on said shaft 136. The lever 20% carries a roller 20 2 which engages a cam; 204 on the camshaft 1-18. The lever 196 carries an abutment 206 which engages the lower side of the lever 2%. The abutment 206 can be adjusted along the lever 1%- by means of a screw 20%.

As the cam 204 is rotated by the shaft 118, the lever 2% is moved downwardly, and in so moving it moves the lever 196 downwardly. The lever 196 moves the link 194 downwardly, and the link moves the lever 182 in the counterclockwise direction so as to move the pitch tool forwardly. When the cam 204 so permits, the springs 1% and 192 move the several parts in the reverse directions. Movements in the reverse directions are limited by a screw 210 which engages an abutment on the frame member 12. The cam 204 preferably comprises two parts that are relatively adjustable anguiarly so that the effective shape of the cam can be changed. The extent of movement of the various parts can be changed by adjusting the abutment 206 relatively to the lever 196. The stop screw 210 can be adjusted to limit the rearward movement of the pitch tool.

The extent of forward movement of the pitch tool is adjustable without changing or adjusting the cam 204. As shown, the link 194' extends loosely through a hole in the lever arm 182 and a sleeve 212 surrounds the link above said lever arm. The upper portion of the link 194 is threaded and a nut 214 on said threaded portion engages the top of the sleeve. When the nut 214 is" adjusted downwardly, the effective length of the link .194 is decreased and the pitch tool is moved forwardly to increase the pitch of the springs.

When springs are to be made with a fixed predetermined pitch, the nut 214 is turned so as to lower the link 194 together with the levers 196 and 200 so that these parts are not operated by the cam 204. Then the screw 211i is turned to move the pitch tool 110 forwardly to the position necessary for the required pitch of the springs. When the pitch is to be varied during the coiling of each spring, the nut 214 is turned to bring the various parts within the control of the cam 204. As the cam turns, the pitch tool 110 is moved forwardly and rearwardly during coiling, so that the pitch is varied in accordance with a pattern determined by the shape or adjustment of the cam 2G4 and by the adjustment of the abutment 206. While the pattern of the pitch variations is determined by the cam 2414 and the abutment 1266, the actual spring pitch can be adjusted, during machine operation if desired, by turning the nut 214. Such turning moves the pitch tool forwardly or rearwardly in addition to any movements effected by the cam 2414.

The shape and position of the cam 2414 are shown schematically and not accurately, and the actual shape and position vary in accordance with the requirements for the particular springs to be made. When one complete spring is made during each reciprocation of the gear segment, the cam 204 is shaped to compensate for the variations in the rate of wire feed as effected by said segment.

'2 Diameter control mechanism Referring particularly to FIGS. 1, 3, 7 and 8, the diameter control mechanism includes the before-mentioned coiling point 106 and means for supporting and controlling said coiling point. The last said means as herein illustrated is in many respects similar to that shown in the Franks and Froelich Patent No. 2,820,505, issued January 21, 1958.

For supporting and moving the coiling abutment 106, there is provided a slide 216 guided for horizontal movement along the front of the frame member '12. Carried by the slide 216 at the front thereof is an approximately horizontal arm 218 which is pivotally movable relatively to said slide about a horizontal longitudinal axis extending transversely of the slide and provided by a bolt 220. As shown in FIG. 8, said bolt 220 extends through an aperture in the slide 216 and there is a bushing 222 on the bolt which fits an aperture in the arm.

The arm 218 has a groove extending lengthwise thereof and open at the front, and a holder 224 is located in said groove. The coiling point 106 is suitably connected with the holder at the right end thereof. The holder is preferably pivoted to the arm 218 for pivotal movement about a vertical axis near the left end of said holder. As best shown in FIG. 7, said axis is ordinarily vertical and is provided by a vertical pivot pin 226 which extends through apertures in the arm and in the holder. The holder 224 is movable to a limited extent about the axis of the pin 226 for the adjustment of the ceiling point 106 forwardly or rearwardly. Screws 228 and 230 are provided for so moving the holder. Secured to the slide 216 is a bracket which carries vertical screws 232 and 234. By means of these screws the arm 218 and the holder 224 and the coiling point 106 can be adjusted vertically.

The slide 216 is movable for moving the coiling point 106 toward and from the arbor 104 and for thus determining the diameter of the spring to be coiled. For a spring of uniform diameter the abutment is held in a fixed position, but when the spring diameter is to be varied during the coiling of each spring, the slide 216 and the parts carried thereby are moved during coiling. For this latter purpose there is provided a bell crank which is at the .rear of the frame member 12 and is movable about the axis of a horizontal longitudinal pin 236. The bell crank has an upwardly extending arm 238 which is connected with the slide 216 by a link 240 in a slot in the frame member 12. The bell crank has an arm 242 in engagement with a generally vertical link 244 which serves to move the bell crank and the slide 216. The bell crank has a third arm 246 connected with a spring 248 which biases the bell crank for counterclockwise movement and which thus biases the slide 216 for movement toward the left.

A screw 250 limits movement of the slide 216 toward the left and the spring 248 tends to hold the slide in engagement with the screw. When the link 244 is inactive, the slide 216 may be adjusted by the screw 250 to set the coiling abutment 106 for a spring of any desired diameter within the capacity of the machine.

The link 244 is connected at its lower end, as shown in F116. 7, with a transverse lever 252 pivotally mounted on said longitudinal shaft 193. A transverse lever 254 is positioned above the lever 252 and is pivotally mounted on said shaft 136. The lever 254 carries a roller 256 which engages a cam 258 on the camshaft 118. The lever 252 carries an abutment 260 which engages the lower side of the lever 254. The abutment 260 can be adjusted along the lever 252 by means of a screw 262.

As the cam 258 is rotated by the shaft 118, the lever 254 is moved downwardly, and in so moving it moves the lever 252 downwardly. The lever 252 moves the link 244 downwardly, and the link moves the bell crank in the clockwise direction so as to move the coiling point 106 toward the arbor 104. When the cam 258 so permits, the

spring 243 moves the several parts in the reverse direction. With the screw 250 backed away, the said diameter cam 258 serves to move or cause the movement of the coiling abutment during coiling so as to vary the spring diameter.

The cam 258 preferably comprises two parts that are relatively adjustable angularly so that the effective shape of the cam can be changed. The extent of movement of the various parts can be changed by adjusting the abutment 260 relatively to the lever 252.

The movement of the coiling point is preferably adjustable without changing or adjusting the cam 258. As shown, the link 244 extends loosely through a hole in the arm 242 and a sleeve 262 surrounds the link above said arm. The upper portion of the link 244 is threaded and a nut 264 on said threaded portion engages the top of the sleeve. When the nut 264 is adjusted downwardly, the effective length of the link 244 is decreased and the coiling point 106 is moved toward the right to decrease the diameter of the springs.

When the springs are to be made with a fixed predetermined diameter, the nut 264 is turned so as to lower the link 244 together with the levers 252 and 254 so that these parts are not operated by the cam 258. Then the screw 250 is turned to move the coiling point 106 toward the right to the position necessary for the required diameter of the springs. When the diameter is to be varied during the coiling of each spring, the nut 264 is turned to bring the various parts within the control of the earn 258. As the cam turns, the coiling point 106 is moved so that the diameter is varied in accordance with a pattern determined by the shape or adjustment of the cam 258 and by the adjustment of the abutment 260. While the pattern of the pitch variations is determined by the cam 258 and the abutment 260, the actual spring diameter can be adjusted, during machine operation if desired, by turning the nut 264. Such turning moves the coiling point toward or from the arbor 104 in addition to any movements effected by the cam 258.

The shape and position of the cam 258 are shown schematically and not accurately, and the exact shape and position vary in accordance with the requirements for the particular springs to be made. When one complete spring is made during each reciprocation of the gear segment, the cam 258 is shaped to compensate for the variations in the rate of wire feed as effected by said segment.

Mechanism for increased feed per spring- FIGS. 3, 9 and 10 As has been stated, the general object of the invention is to make it possible for a spring coiling machine of the oscillating segment type to make springs requiring longer wire lengths than are available as the result of wire feeding during only one cycle and as the result of only one oscillation of the segment. To this end, provision is made for effecting exactly one camshaft rotation within each successive period of time required for an integral plurality of sequential gear segment oscillations. The cut-off mechanism is operated by the camshaft and the gear segment therefore makes an integral plurality of sequential oscillations between each two operations of the cut-off mechanism.

The gear 12 which drives the camshaft 118 is connected therewith indirectly rather than directly. One mechanism for connecting the gear with the shaft is shown in FIG. 3, and another mechanism for this purpose is shown in FIGS. 11 to 15 and is hereinafter described. The said mechanism shown in FIG. 3 rotates the camshaft at a speed substantially less than that of the gear and continuously during a plurality of segment oscillations or during a plurality of cycles, but the reduced speed and continuous rotation are not essential as will be hereinafter apparent.

In said FIG. 3 mechanism, the gear 124 is secured to a sleeve 266 which surrounds the shaft 118 and is rotatable thereon, said sleeve being within a bearing in the frame member 14. The sleeve at its rear end is provided with gear teeth 268. The gear teeth 268 mesh with a gear 270 secured to a sleeve 272 rotatable on a stud 274 which is carried by the rear frame member 14. Intermeshing change gears 276 and 278 are removably connected respectively with the sleeve 272 and the shaft 118. The gear ratios are such that the camshaft rotates more slowly than the gear 124 so that the segment 74 makes an integral plurality of oscillations during each complete rotation of the camshaft. As shown, the gears 268 and 278 have a 1 to 2 ratio, and the gears 276 and 278 have a l to 3 ratio, the result being a final ratio of 1 to 6. Therefore, the camshaft 118 makes onesixth of a rotation during each segment oscillation, or otherwise stated, there are six cycles or six segment oscillations during each camshaft rotation. By substituting other gears for the gears 276 and 278, other final speed ratios may be obtained, such as 1 to 4 or 1 to 2.

The cut-off mechanism is operated by the camshaft 118 as previously explained. The cut-oil? mechanism is timed to effect cut-off during the reverse rotation of the feed gear 88 that next follows the completion of the spring, that is, during the next following period during which no wire feeding takes place. When the gearing is as shown in FIG. 3, the gear segment will make six oscillations between each two operations of the cut-off mechanism. Thus the available length of wire is six times as long as that which would be available in a conventional machine. 'It will of course be understood that the wire length fed during each segment oscillation can be accurately determined by adjusting the crankpin 86. It is therefore possible by adjusting said crankpin to accurately determine the total Wire length fed during a plurality of oscillations, that is, the total wire length fed between each two cut-off operations.

When the segment makes more than one oscillation for each spring, that is, for each camshaft rotation, it is not readily feasible to effect pitch and diameter changes throughout the entire length of each spring. This is due to the fact that the rate of wire feed varies between zero and maximum a plurality of times during the coiling of each spring. However, it is readily possible to utilize the pitch and diameter mechanisms to eifect pitch and diameter changes in a few spring coils near the leading and trailing ends of a spring.

One or both of the cams 284 and 258 may be so shaped and so related to the cut-off cam 14!) that they serve immediately before cut-01f to effect any required pitch and diameter changes in a few coils in the trailing end of the spring about to be cut off. One or both of said cams 204 and 252 may be additionally so shaped and so related to the cutoff cam 140 that they serve immediately after cut-off to eifect any required pitch and diameter changes in a few coils in the leading end of the spring that is being started.

In order that a machine embodying the invention may also be used as a conventional machine with the shaft 118 rotating at the same speed as the gear 124, the gears 278, 276 and 278 may be removed and an adapter 280 may be substituted for the gear 278 as shown in FIG. 9. The adapter 288 is directly connected with the sleeve 266 by a pin 282, and thus the shaft 118 is driven at the same speed as the gear 124.

It is sometimes desired to eifect continuous coiling without any automatic cut-off operation. For continuous coiling, the crankpin 86 is adjusted to its dead center position so that the segment 74 is not operated. The gears 278, 276 and 278 are removed, and a special gear 284 is substituted for the gear 278 as shown in FIG. 10. An idler gear 286 carried by a stud 288 projecting rearwardly from the frame member 14 meshes with the special gear 284 and with the gear 61) which drives the feed rolls. When the gears 284 and 286 are in use, motion is transmitted from the continually ro- 10 tating gear 124 through the gears 284, 286 and 60 so as to continually rotate the feed rolls.

Alternative mechanism for increased feed per spring- FIGS. 11 to 15 FIGS. 11 to 15 show a driving mechanism from the gear 124 to the shaft 118 which is an alternative to the driving mechanism shown in FIG. 3, and which is ordinarily found preferable. This alternative driving mechanism includes a single rotation clutch, and said mechanism, instead of rotating the camshaft slowly, rotates said shaft at the same speed as the gear 124, but intermittently. During the making of each spring, the gear segment makes a selected integral number of oscillations independently of the camshaft and then the camshaft makes exactly one rotation at conventional speed and in unison with one segment oscillation. Otherwise stated, t-he rotation of said camshaft is started once and makes exactly one rotation during each of a succession of cycles with a predetermined integral plurality of cycles in each series.

The alternative mechanism includes a one-rotation clutch 290 and the presently preferred clutch and the parts associated therewith will now be described. The gear 124 is secured to a sleeve 291 generally similar to the sleeve 266, but having no gear teeth 268. The shaft 118 has a portion 292 of reduced diameter which extends beyond the sleeve 291. A generally cylindrical body 294 forming a part of the clutch 290 is fixedly connected to the shaft extension 292. Interposed between the clutch body 294 and the sleeve 291 and secured to the latter is a disc 296 having one radial groove 298 in the face thereof adjacent the clutch body.

Longitudinally movable in a groove in the clutch body 294 is a clutch bolt 300 having a tooth at the front adapted to enter the groove 298 in the disc 296. The bolt is shown in its engaged position and a spring 302 biases the bolt from its retracted position and toward the left to said engaged position so that its tooth is entered in the groove 298 in the disc 296. The body 294 has an annular groove 304 and the bolt 380 has a notch 306 which fully registers with the groove when the bolt is in its retracted position. A lever 308 is provided which is carried by a sleeve 310 oscillable on a pivot pin 312. The end portion of the lever is normally entered in the groove 304 and the bolt and the lever have mating beveled faces at 3 14 and 315. A spring 316 tends to hold the sleeve 3 10 and the lever 308 so that the latter is entered in the groove.

Carried by the sleeve 310 is a lever 318 connected with the movable core of a solenoid 320. When the solenoid is not energized, the spring 316 holds the parts in the positions shown. As will be evident from FIG. 14, the shaft 118 and the clutch parts have nearly completed a revolution. -As the shaft and clutch parts continue to rotate, the beveled face 314 on the bolt engages the beveled face 315 on the lever and the bolt is forced toward the right so as to be withdrawn from the groove 298. Thereupon the shaft 118 is held in a definite predetermined position, but the sleeve 291 is free to continue its rotation. When the solenoid 320 is thereafter momentarily energized, the lever 318 and the sleeve 310 and the lever 308 are moved in the counterclockwise direction, as viewed in FIG. 12, and the lever 308 is withdrawn from engagement with the bolt 300 and the bolt is then moved by the spring 302 to enter the groove 298 as soon as said groove comes into register. The entry of the bolt 300 in the groove 298 starts the rotation of the camshaft, but before there has been one complete rotation the solenoid is de-energized to restore the lever 308 to its position in the annular groove. As the bolt 300 again moves beyond the position shown in FIG. 14, it again engages the lever 388 and the beveled faces at 314 and 315 again return the bolt to its retracted position. Thus the shaft is given exactly one rotation and is then stopped and held in a predetermined position.

The solenoid 320 can be variously energized, and a means for the purpose is shown in said FIGS. 11, 12 and 15. An alternative means is shown in FIGS. 19, 20 and 21.

As shown in said FIGS. 11, 12 and 15, there is provided a counting device 322 having a normally open switch 324 in series with the solenoid 320. The counting device is operable to count cycles or segment oscillations. FIG. 12 shows the counting device 322 mounted on a bracket above the clutch 290. The counting device has a rotatable shaft 326 which is rotated in synchronism with the sleeve 291 by suitable means such as a chain 328 engaging a sprocket wheel 330 on said sleeve 291 and a sprocket wheel 332 on said shaft 326. Included in the counting device 322 is a counter, not shown, which serves after a predetermined number of revolutions of the shaft 326 to momentarily close the switch 324 and to thus energize the solenoid 320 and effect rotation of the camshaft. The counter can be set to close the switch 324 after any predetermined integral number of rotations of the shaft 325, that is, after any predetermined number of reciprocations of the gear segment. The counting device is so constructed that it holds the switch 324 closed during a sufficient period to enable the shaft 118 to start its rotation before the lever 303 is released. The counter is automatically reset to zero after said predetermined number of operations so as to be ready for making the next spring.

It will be seen that by setting the counter and by adjusting the throw of the gear segment 74, any desired length of wire can be fed. Furthermore, the camshaft 118 is rotated at normal speed and the cut-off device is more effectively operated than it would be by the slowly moving camshaft shown in FIG. 3.

FIGS. 16, 17 and 18 schematically show the timing of the action of the gear segment and of the several mechanisms in feeding, shaping and cutting the wire during a plurality of segment oscillations or cycles. FIG. 16 schematically shows the gear segment itself and FIG. 17 schematically shows the spring lengths and locations at the ends of the several half-cycles. For purposes of the explanation, it will be assumed that each cycle starts with the crankpin 84 at position A in FIG. 16. With the crankpin in this position the segment is approximately midway of its movement in the reverse direction. It will also be assumed that the machine is set to make springs with a length corresponding to four segment oscillations or four cycles. It will be further assumed that the machine is adjusted to make spring shaped at their ends, as for instance by having their end portions reduced in diameter. The pitches of the end portions of springs may also be changed.

Referring particularly to FIG. 16, feeding is effected during the motion of the crankpin 84 from B to D, and there is no feeding during the motion from D to B. The parts for engaging the clutch 290 are so timed in relation to the gear segment that the clutch is engaged and the camshaft rotation started when the crankpin is in position C, that is, half-way through the feed portion of the fourth cycle. The shaft 326 and the counter are so timed that the first impulse for engaging the clutch 290 to start rotation of the camshaft is effected when the crankpin is at or about position E; but as has been stated, the shaft does not actually start until position C is reached. The exact location of position E is not critical, but it must be so located as to allow time for the solenoid and the clutch parts to move into positions for starting shaft rotation at position C.

In describing FIG. 17, it will be assumed that the first cycle starts not only with the crankpin in position A but also with clutch 290 engaged so that the camshaft is rotating. The fourth cycle ends with the crankpin again in position A and with the camshaft again rotating.

Section a of FIG. 17 shows the portion of a spring S made during the first half of the first cycle. The cam- 12 shaft is making the second half of its single continuou rotation, which rotation stops when position C is reached. Inasmuch as the camshaft is rotating, the pitch and diameter mechanisms can be operated to change the shape of the leading end portion of the spring.

Sections b, c, d and a respectively show the additional portions of the spring S made during the second half of the first cycle, during the entire second cycle, during the entire third cycle, and during the first half of the fourth cycle. The camshaft is idle during these four stated periods.

Section 1 shows the portion of the spring S made during the second half of the fourth cycle, the camshaft having been again started with the crankpin at C in said fourth cycle and said camshaft making the first half of its single continuous rotation. Inasmuch as the camshaft is rotating, the pitch and diameter mechanisms can be operated to change the shape of the trailing end portion of the spring. At the end of the second half of the fourth cycle, the cut-off mechanism is operated by the camshaft to cut off the completed spring, cut-off being effected with the crankpin at or about position A.

FIG. 18 constitutes a summary of the several sections of FIG. 17, this view clearly showing the portions of the spring made during the respective cycles. It will be observed that shaping at the leading end or at the trailing end of each spring is effected during a half rotation of the camshaft and in a half cycle which is in immediately sequential relationship with the operation of the cut-off mechanism.

The mechanism shown in FIGS. 11 to 15 makes it conveniently possible to adapt the mechanism for conventional operation, wherein the camshaft makes one complete rotation during each segment oscillation. As shown in FIG. 12, a pin 333 is provided at the left of the lever 308, and the spring 316 can be shifted to engage said pin 333 as shown by dotted lines at 316. When the spring is engaged with the pin 333, it holds the lever 308 out of its operative position. With the lever 308 inoperative, the clutch 290 is continually engaged and the camshaft 118 rotates in unison with the gear 124-.

For continuous coiling, the crankpin 86 is adjusted to its dead center position so that the segment 74 is not operated. The disc 296 and the clutch body 294 are removed and if necessary the counting device 322 is also removed. A special gear is connected in place of the disc 296, this special gear not being shown but being similar to the gear 234 shown in FIG. 10. The power transmission for continuous coiling is otherwise similar to that shown in FIG. 10.

Second alternative mechanism for increased feed per springFIGS. 11 to 14 and FIGS. 19 to 21 A second alternative mechanism is shown in FIGS. 19 to 21 which is the same as concerns the parts shown in FIGS. 11 to 14, but which includes a different means for energizing the solenoid 320. In lieu of a counting device such as 322, means is provided for enabling each nearly completed spring to effect energization of the solenoid 320.

A longitudinal trough, generally indicated at 334 in FIG. 19, is provided for receiving and supporting each spring as it is coiled and cut off. The trough structure includes a longitudinal bar 336, which is supported at its rear end by a vertical screw 338 carried by a bracket 340 secured to the front frame member 12 of the machine and which is supported near its front end by a vertical screw 342 on a mast 344 having a floor engageable pedestal 346. The trough proper is V-shaped and it comprises two oppositely inclined plates 348 and 350. The plate 348 is fixedly connected with bar 336 and the plate 350 is pivoted for lateral movement about a horizontal axis at 352.

Secured to the bar 336 are longitudinally spaced blocks 354, 354, each of which carries a bar 356 that projects 13 toward the left as viewed in FIG. 19. Pivoted to each bar 356 at the said axis 352 is a bar 358 to the lower portion of which the plate 350 is secured. The respective blocks 354 and bars 358 are connected by springs 360' which tend to hold the several parts in the positions shown in FIG. 19.

Pivotally connected with an extended rear portion of one of the bars 356 is a bell crank 362. The corresponding one of the bars 358 has an upward extension 364 which is connected by a link 366 with one arm of said bell crank 362. The other arm of the bell crank is con nected by a link 368 with the core of a solenoid 370 fixedly supported on said bar 336. When the parts are in the positions shown by full lines, a spring such as S is supported on the trough. When the solenoid 37% is energized, the plate 356 is swung about the axis of 352 and toward the left to the positions shown in dotted lines and the spring S is released to move downwardly by gravity.

A normally open limit switch LS is actuated, by means not shown, so as to be momentarily closed upon each action of the cut-off mechanism. The switch LS is conected in series with the solenoid 370 as shown in FIG. 20. Upon each action of the cut-off device, the solenoid 370 is energized to release the completed spring S from the trough 324. A push button switch PB may be provided in parallel with the switch LS to enable a spring to be manually released when necessary.

Carried by the trough plate 348 is means operable by the leading end of a partially completed spring for starting the operation of the camshaft. This means is preferably an electrical contact device, and said device is shown as being a longitudinally adjustable contact 372. The contact 372 is insulated from said plate 348 and a flexible conductor 374 is connected with said contact. As a spring such as S is coiled and moved forwardly through the trough, said spring engages the contact 372 to close an electric circuit.

Referring particularly to FIG. 21, it will be seen that engagement of a spring, such as S, with the contact 372 closes a circuit through an electronic relay ER, having normally separated contacts ER The contacts ER are connected in series with a relay R having normally separated contacts R The contacts R are connected in series with the previously described solenoid 320. When a spring S moving along the trough reaches the contact 372, a circuit is closed through the realy ER, which closes a circuit through the realy R. The relay R closes a circuit through the solenoid 320 which then effects engagement of the clutch 290 to start rotation of the camshaft 118. The contact 372 is so postioned that the solenoid is engaged at or about position E as shown in FIG. 16, but the camshaft does not actually start until position C is reached.

A push button switch PB may be provided in parallel with the contact 372, so that the rotation of the camshaft may be manually started.

The timing and the sequence of steps for the mechanism as shown in FIGS. 19 to 21 is the same as shown in FIGS. 16 to 18 in connection with the mechanism as shown in FIGS. 11 to 15. A repetition of the explanation is unnecessary, but it should be particularly observed that the position of the contact 372 is not critical. As stated, the contact is placed to energize the solenoid 320 about at E in FIG. 16, but there can be considerable variation as to position E inasmuch as camshaft rotation does not start until position C is reached.

Summary of advantages Any one of the three mechanisms shown respectively in FIGS. 2, 9 and 10 and in FIGS. 11 to 13 and in FIGS. 11 to 14 and 19 to 21, enables a machine of the segment type to coil springs requiring a greater length of wire than that which could be fed by a conventional segment type machine. It is therefore possible to obtain the accuracy of a segment type machine in the coiling of long springs.

It is furthermore possible, particularly with the second and third mechanisms, to readily effect shaping of the coils at one or both ends of each spring. The camshaft that controls the shaping always rotates at a speed having a fixed relationship with the rate of segment oscillation, and therefore the character of the shaping is always the same and is not varied by variations in camshaft speed. Furthermore, the action of the oscillating segment is such.- that the wire feeding is relatively slow at the beginning and at the end of each feeding movement, and thus allows ample time for effecting the required shaping. This is in contrast with the action of a clutch type machine, wherein the wire feeding starts suddenly and at full speed.

Under some circumstances each of the mechanisms embodying the invention has an important advantage, even when the wire length is within the capacity of a standard machine. When a spring is to be made from very large wire, a standard segment type machine may not have sufficient power to effect coiling when the machine is adjusted to feed the wire at the speed necessary to provide the required wire length. When this problem is encountered with a machine embodying the invention, the machine may be adjusted to feed perhaps half as much wire per cycle and further adjusted to effect cut-off after perhaps two cycles. Thus the coiling of the large wire is effected at one-half of the speed and within the power capacity of the machine.

The invention claimed is:

1. In a cyclically operable spring coiling machine, the combination of an oscillable gear segment, continually operating means for effecting one complete segment oscillation during each of the cycles of machine operation, a feed gear meshing with the gear segment and rotated thereby in a feeding direction and in the reverse direction during each cycle, each cycle of the machine starting when the segment is approximately midway of its movement in the reverse direction, a feed shaft, a unidirectional clutch operably connected with said feed shaft and feed gear and serving during rotation of the latter in the said feeding direction thereof to rotate the feed shaft in the feeding direction, feed rolls operably connected with the feed shaft and engageable with a length of wire to effect wire feeding during rotation of the feed shaft, means engageable by the wire during each feeding movement thereof to effect wire coiling so as to thereby form a portion of a spring, a rotatable camshaft, camshaft driving means for effecting exactly one rotation of said camshaft during a period of time equal to that of one cycle, second operating means connected to said driving means and automatically operable to start rotation of said camshaft during each of a succession of series of cycles with a predetermined integral plurality of cycles in each series, said second operating means serving to start said camshaft approximately at the beginning of the second half of the last cycle of each series and with the segment approximately midway of its movement in the feeding direction, and a cut-off mechanism operable by said camshaft approximately after a half rotation thereof and approximately at the end of the second half of the last cycle to cut the wire after the completion of each spring.

2. In a cyclically operable spring coiling machine, the combination of an oscillable gear segment, continually operating means for effecting one complete segment oscillation during each of the cycles of machine operation, a feed gear meshing with the gear segment and rotated thereby in a feeding direction and in the reverse direction during each cycle, each cycle of the machine starting when the segment is approximately midway of its movement in the reverse direction, a feed shaft, a unidirectional clutch operably connected with said feed shaft and feed gear and serving during rotation of t e latter in the said feeding direction thereof to rotate the feed shaft in the feeding direction, feed rolls operably connected with 1 5 the feed shaft and engageable with a length of wire to effect wire feeding during rotation of the feed shaft, means engageable by the wire during each feeding movement thereof to effect wire coiling so as to thereby form a portion of a spring, a rotatable camshaft, camshaft driving means for effecting exactly one rotation of said camshaft during a period of time equal to that of one cycle, second operating means connected to said driving means and automatically operable to start rotation of said camshaft during each of a succession of series of cycles with a predetermined integral plurality of cycles in each series, said second operating means serving to start said camshaft at the beginning of the second half of the last cycle of each series and with the segment midway in the feeding direction, and a cut-off mechanism operable by said camshaft after a half rotation thereof and at the end of the second half of the last cycle to cut the wire after the completion of each spring.

3. A cyclically operable spring coiling machine as set forth in claim 2, wherein an adjustable counting device is provided which is operable to count the segment oscillations, and wherein there is provided a means enabling the counting device to control said predetermined plurality of cycles in each series.

4. In a cyclically operable spring coiling machine, the combination of an oscillable gear segment, continually operating means for effecting one complete segment oscillation during each of the cycles of machine operation, a feed gear meshing with the gear segment and rotated thereby in a feeding direction and in the reverse direction during each cycle, each cycle of the machine starting when the segment is approximately midway of its movement in the reverse direction, a feed shaft, a unidirectional clutch operably connected with said feed shaft and feed gear and serving during rotation of the latter in the said feeding direction thereof to rotate the feed shaft in the feeding direction, feed rolls operably connected with the feed shaft and engageable with a length of wire to elfcct wire feeding during rotation of the feed shaft, means engageable by the wire during each feeding movement thereof to effect wire coiling so as to thereby form a portion of a spring, a rotatable camshaft, camshaft driving means for effecting exactly one rotation of said camshaft during a period of time equal to that of one cycle, second operating means connected to said driving means and automatically operable to start rotation of said camshaft during each of a succession of series of cycles with a predetermined integral plurality of cycles in each series, said second operating means serving to start said camshaft approximately at the beginning of the second half of the last cycle of each series and with the segment approximately midway in the feeding direction and said second operating means serving to stop said shaft approximately at the end of the first half of the first cycle of the next following series and with the segment again approximately midway of its movement in the feeding direction, a cutoff mechanism operable by said camshaft after a half rotation thereof and at the end of the second half of the last cycle to cut the wire after the completion of each spring, and mechanism operable by said camshaft during a half rotation thereof and in a half cycle which is in immediately sequential relationship with the operation of the cut-off mechanism which mechanism is adapted for changing the shape of the coils of one end portion of the spring.

5. In a cyclically operable spring coiling machine, the combination of an oscillable gear segment, continually operating means for effecting one complete segment os cillation during each of the cycles of machine operation, a feed gear meshing with the gear segment and rotated thereby in a feeding direction and in the reverse direction during each cycle, each cycle of the machine starting when the segment is approximately midway of its movement in the reverse direction, a feed shaft, a unidirectional clutch operably connected with said feed shaft and feed gear and serving during rotation of the latter in the said feeding direction thereof to rotate the feed shaft in the feeding direction, feed rolls operably connected with the feed shaft and engageable with a length of wire to effect wire feeding during rotation of the feed shaft, means engageable by the wire during each feeding movement thereof to effect wire coiling so as to thereby form a portion of a spring, a rotatable camshaft, camshaft driving means for effecting exactly one rotation of said camshaft during a period of time equal to that of one cycle, second operating means connected to said driving means and automatically operable to start rotation of said camshaft during each of a succession of series of cycles with a predetermined integral plurality of cycles in each series, said second operating means serving to start said camshaft at the beginning of the second half of the last cycle of each series and with the segment midway in the feeding direction and said operating means serving to stop said camshaft at the end of the first half of the first cycle of the next following series and with the segment again midway in the feeding direction, a cut-off mechanism operable by said camshaft after a half rotation thereof and at the end of the second half of the last cycle to cut the wire after the completion of each spring, and mechanism operable by said camshaft during the first half of its rotation and in the second half of said last cycle and adapted for changing the shape of the coils of the trailing portion of the spring that is being completed which mechanism is also operable by said camshaft during the second half of its rotation and in the first half of the first cycle of the next following series and adapted for changing the shape of the coils in the leading portion of the next following spring that is being started.

6. A cyclically operable spring coiling machine as set forth in claim 5, wherein an adjustable counting device is provided which is operable to count the segment oscillations, and wherein there is provided a means enabling the counting device to control said predetermined plurality of cycles in each series.

References Cited in the file of this patent UNITED STATES PATENTS 

